EP0496945B1 - Drehanoden-Röntgenröhre - Google Patents

Drehanoden-Röntgenröhre Download PDF

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Publication number
EP0496945B1
EP0496945B1 EP91116669A EP91116669A EP0496945B1 EP 0496945 B1 EP0496945 B1 EP 0496945B1 EP 91116669 A EP91116669 A EP 91116669A EP 91116669 A EP91116669 A EP 91116669A EP 0496945 B1 EP0496945 B1 EP 0496945B1
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EP
European Patent Office
Prior art keywords
rotary
cylinder
anode
stationary
ray tube
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP91116669A
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English (en)
French (fr)
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EP0496945A1 (de
Inventor
Katsuhiro C/O Intellectual Property Division Ono
Hidero C/O Intellectual Property Division Anno
Hiroyuki C/O Intellectual Property Div. Sugiura
Takayuki C/O Intellectual Property Div. Kitami
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Toshiba Corp
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Toshiba Corp
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Publication date
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Publication of EP0496945A1 publication Critical patent/EP0496945A1/de
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Publication of EP0496945B1 publication Critical patent/EP0496945B1/de
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Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/06—Sliding surface mainly made of metal
    • F16C33/10—Construction relative to lubrication
    • F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
    • F16C33/109—Lubricant compositions or properties, e.g. viscosity
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01J—ELECTRIC DISCHARGE TUBES OR DISCHARGE LAMPS
    • H01J35/00—X-ray tubes
    • H01J35/02—Details
    • H01J35/04—Electrodes ; Mutual position thereof; Constructional adaptations therefor
    • H01J35/08—Anodes; Anti cathodes
    • H01J35/10—Rotary anodes; Arrangements for rotating anodes; Cooling rotary anodes
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01J—ELECTRIC DISCHARGE TUBES OR DISCHARGE LAMPS
    • H01J35/00—X-ray tubes
    • H01J35/02—Details
    • H01J35/04—Electrodes ; Mutual position thereof; Constructional adaptations therefor
    • H01J35/08—Anodes; Anti cathodes
    • H01J35/10—Rotary anodes; Arrangements for rotating anodes; Cooling rotary anodes
    • H01J35/101—Arrangements for rotating anodes, e.g. supporting means, means for greasing, means for sealing the axle or means for shielding or protecting the driving
    • H01J35/1017—Bearings for rotating anodes
    • H01J35/104—Fluid bearings
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01J—ELECTRIC DISCHARGE TUBES OR DISCHARGE LAMPS
    • H01J2235/00—X-ray tubes
    • H01J2235/10—Drive means for anode (target) substrate
    • H01J2235/1046—Bearings and bearing contact surfaces
    • H01J2235/106—Dynamic pressure bearings, e.g. helical groove type

Definitions

  • the present invention relates to a rotary-anode type X-ray tube, more particularly to improvement of the rotary structure for rotating an anode target.
  • a disk-like anode target is supported by a rotary structure and a stationary structure.
  • the rotary structure is connected to the stationary structure by a bearing portion.
  • An electron beam emitted from a cathode is applied to the anode target while the anode target is rotated at a high speed by energizing an electromagnetic coil arranged outside a vacuum envelope, thus irradiating X-rays.
  • the bearing portion is constituted by a rolling bearing such as a ball bearing or a hydrodynamic pressure type sliding bearing which has bearing surfaces with spiral grooves on the bearing surface and uses a metal lubricant consisting of, for example, gallium (Ga) or gallium-indium (Ga-In-Sn) alloy, which is liquified during an operation.
  • a rolling bearing such as a ball bearing or a hydrodynamic pressure type sliding bearing which has bearing surfaces with spiral grooves on the bearing surface and uses a metal lubricant consisting of, for example, gallium (Ga) or gallium-indium (Ga-In-Sn) alloy, which is liquified during an operation.
  • the rotary-anode type X-ray tubes using the sliding bearing are disclosed in, for example, Published Examined Japanese Patent Application No. 60-21463 and Published Unexamined Japanese Patent Application Nos. 60-97536, 60-113817, 60-117531, 61-2914, and 62-287555.
  • the rotor assembly includes a rotary shaft supporting the anode target and made of a metal having a high melting point, a cylindrical inner core functioning as a rotor of a motor, fixed to the rotary shaft, and made of a ferromagnetic material such as iron, and an outer cylinder made of a material having a high electric conductivity such as copper.
  • the inner core is fitted in the outer cylinder and brazed to the outer cylinder.
  • a stationary shaft is inserted into the rotary cylinder.
  • a bearing connects the stationary shaft and the rotary cylinder.
  • the rotor is rotated at a high speed, according the theory of an induction motor, when a rotating magnetic field is applied to the rotor from a stator outside the tube.
  • the bearing surface is hardly abraded and rotational noises are hardly produced.
  • the X-ray tube the following problems occur. While the X-ray tube operates, the rotor cylinder supporting the anode target is heated due to the heat transmitted from the target. Therefore, the hydrodynamic pressure type sliding bearing is also heated. Thus, when the bearing is filled with liquid metal, various problems may occur. For example, the rotational performance of the bearing is degraded due to a change of the bearing gap distance, and the liquid metal reacts on the bearing material because it is active. Therefore, as disclosed in the above-identified patent applications, the above problem can be solved by forcibly cooling the sliding bearing with circulating coolant. To this end, the X-ray tube apparatus must have coolant circulating paths and a coolant circulation system. Thus, the system can be use only for a special equipment because it is not compatible with the conventional X-ray tube.
  • Prior art document JP-A-2-144836 discloses a rotary anode X-ray tube.
  • an anode target is firmly attached to the upper portion of a supporting member which has the side of the anode target of a cylindrically-formed rotor integrally bonded at the lower portion thereof.
  • a cylindrically-formed rotary shaft is bonded at the lower portion and supported by a supporting shaft via ball bearings so as to be rotationally moved.
  • prior art document DE-A-32 45 455 discloses an X-ray tube apparatus which also uses a ball bearing and wherein heat insulating gaps are formed between first and second rotary members.
  • Prior art document EP-A-0 141 475 which corresponds to already mentioned published unexamined Japanese patent application 60-117531 describes an X-ray tube apparatus wherein a liquid metal lubricated helical-groove bearing is provided with a push-pull bearing at one or both end faces of a bearing member. Consequently, the bearing member need not be further secured so that, notably in the case of suitable cooling of the anode disc and the bearing, extremely precise positioning of the radiation object point in the tube can be achieved.
  • prior art document EP-A-0 351 225 discloses an X-ray tube apparatus comprising a vacuum envelope for maintaining an internal vacuum, a cathode disposed in said vacuum envelope, a rotating anode disposed in said vacuum envelope facing said cathode and being spaced therefrom, a support member for supporting said rotating anode and a cylindrical rotor co-operating with a stator.
  • a cylindrical first member disposed radially inwardly of said rotor, and a second member partially concentrically received in an axial chamber provided in the first member.
  • At least one separation type ball bearing is interposed between the first and second members for supporting a rotating motion therebetween.
  • This ball bearing has separable inner and outer races, one of said inner and said outer race being open at an axial end thereof, and a through-hole leads from a position near the openable end of the one race to an outer surface of said first or said second member.
  • the present invention provides a rotary anode type X-ray tube as specified in claim 1 or claim 5.
  • Figs. 1 and 2 show an embodiment of the rotary anode type X-ray tube according to the present invention.
  • a disk-like anode target 11 made of heavy metal is secured to a rotary shaft 13 which is fixed to one end of a cylindrical rotor assembly 12 by a securing screw 14.
  • a cylindrical stationary shaft 15 is fitted into the cylindrical rotor assembly 12.
  • a ring block 16 is secured at the opening section of the rotor assembly 12 to seal the inner space of the rotary assembly 12.
  • the mounting portion 17 of the fixed shaft 15 is air-tightly connected to a glass vacuum envelope 18.
  • the vacuum envelope 18 has an X-ray emitting window 18a.
  • the X rays irradiated from the anode target 11 can pass through the window 18a.
  • a cathode assembly 19 for radiating an electron beam is installed in the vacuum envelope 18 and faces the anode target 11.
  • a hydrodynamic pressure type sliding bearing 20 is provided between the rotor assembly 12 and the stationary shaft 15. Spiral grooves of herringbone pattern are formed in the outer peripheral surface 15a of the stationary shaft 15, constituting radial bearing. Spiral grooves of the same pattern are formed in the both end faces of the stationary shaft 15, constituting a thrust bearing.
  • the rotor assembly 12 has flat and smooth inner surfaces opposing the outer peripheral surface 15a and the end faces of the stationary shaft 15. Spiral grooves can be formed in the inner surfaces of the rotary 12.
  • the bearings have a gap of approx. 20 ⁇ m, between the bearing surfaces of the rotor assembly 12 and stationary shaft 15.
  • the gap and spiral grooves are filled with liquid metal lubricant (not shown) such as a gallium-indium-tin (Ga-In-Sn) alloy.
  • the lubricant is liquified by the heat produced during a rotating operation.
  • a stator 30 having electromagnetic coils surrounds the rotor assembly 12, outside the vacuum envelope 18.
  • a rotating magnetic field is generated by the stator 30.
  • the rotary anode 11 is rotated by the rotating magnetic field at a high speed in the direction of arrow P.
  • the electron beam emitted from the cathode assembly 19 is applied to the anode target 11, which emits X rays.
  • the anode target 11 also generates heat. The most of the heat is dissipated by radiation. The remaining heat is transmitted to the bearing 20 through the rotor assembly 12 and dissipated to the outside of the tube from the mounting portion 17 through the fixed shaft 15.
  • the first cylindrical rotary member 22 is fitted in an outermost cylindrical member 24 made of copper.
  • the first rotary member 22 and outermost cylindrical member 24 are brazed each other, and the first rotary member 22 and the second rotary member 23 are also brazed each other at the end portions 25 remote from the anode target 11, so that the unit rotary assembly 12 is formed.
  • a heat-insulating gap 26 extending along the axis is formed between the first rotary member 22 and second rotary member 23. When the outside diameter of the rotor 12 is approx. 38 mm, the gap 26 is about 0.5 mm.
  • Four small projections 27 are formed on the peripheral end surface of the second rotary member 23 at an interval of 90° around the axis.
  • projections 27 are set in contact with the inner surface of the first rotary member 22, keeping the coaxial arrangement of the first and second rotary members 22 and 23 and applying a mechanical stability to the rotary assembly.
  • the contact area between the small projections 27 and the first rotary member 22 is small, and the resistance to heat transfer is large, minimizing the heat transfer.
  • the ring flange 16 is secured to the opening portion of the second rotary member 23 by a plurality of screws.
  • the heat produced by the anode target 11 is transferred to the first rotary member 22 and conducted to the second rotary member 23 through the small projections 27.
  • the portion has a large heat resistance
  • the heat is conducted mainly to the second rotary member 23 through the brazed portion 25 and the stationary shaft 15 through the bearing gaps.
  • the brazed portion is sufficiently remote from the anode target 11.
  • the heat conductive path is relatively long, extending from the anode target 11 to the brazed portion 25.
  • the first rotary member 22 is made of a material having a small heat conductivity. Hence, the heat conductive path has a large heat resistance. Therefore, the temperature rise in the bearing is minimized.
  • each member can independently expand and contract because the portions of the members, other than the brazed portion, are only mechanically fitted to each other. Therefore, the stress resulting from thermal expansion difference does not concentrate on a particular portion, and stable operation is maintained.
  • the temperature in the sliding bearing 20 is lower by approx. 130°C the temperature of a bearing in the X-ray structure having no gap between the first and second rotary members.
  • the resonance frequency of the rotor can therefore be increased to, for example, 200 Hz or more, and a structure standing high-speed rotation can be obtained.
  • a cylindrical rotor 12 is installed at the center, which rotates together with the anode target 11, and a cylindrical fixed shaft 15 surrounds the rotor 12.
  • the one end of the fixed shaft 15 has a cylindrical hole.
  • a rotary shaft 13 passes through this hole.
  • the opening portion is closed by a disk block 31.
  • the fixed shaft 15 and block 31 are secured to an anode support 17 by a plurality of screws.
  • Spiral grooves 21 are formed in the block 31 contacting the end face of the rotor 12.
  • a ferromagnetic cylinder 32 functioning as the rotor of a motor, and an outermost cylinder 24 made of copper fitted to the outside of the cylinder 32 are arranged on the outer periphery of the fixed shaft 15.
  • the rotary shaft 13 is mechanically and securely fixed to the cylinder 32.
  • the rotary shaft 13 supporting the anode target 11 is secured to the first cylindrical rotary member 33 and the cylindrical second rotary member 34, which is coaxially fitted to the first rotary member 33 and whose outer surface serves as a sliding bearing surface, is installed on the outer periphery of the first rotary member 33.
  • the first rotary member 33 and the second rotary member 34 are connected at that end of the heat conducting path which is remote from the anode target 11. That is, they are integrated with the brazed portion 25 at the thermally remote end.
  • a heat insulating gap 26, extending in the axial direction, is formed between the first cylindrical portion 33 and the second cylindrical portion 34.
  • the outer periphery surface and the end faces of the second rotary member 34 compose bearing surfaces of the hydrodynamic pressure type sliding bearing, since herringbone-pattern spiral grooves 21 are formed in these surfaces.
  • the heat conducting path from the anode target to the sliding bearing surface has a large heat resistance.
  • the heat insulating gap 26 ranges from 0.1 to 1 mm in the radius direction.
  • a heat insulating cylinder 35 made of a heat insulating material having a low heat conductivity, such as a ceramic, is interposed between the first and rotary members 22 and 23.
  • the first and second rotary members 22 and 23 are brazed together at a portion 25 remote from the anode target 11 in a same manner as in shown in Fig. 1.
  • the heat insulating cylinder can be so formed as to coat a heat insulating material on the inner surface of the first rotary member 22 or on the outer surface of the second rotary member 23.
  • the present invention makes it possible to suppress the temperature rise of the bearing. Therefore, the gap of the sliding bearing surface hardly changes, the reaction between active liquid metal and bearing material is prevented, and stable sliding-bearing rotational performance is maintained for a long time.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Mechanical Engineering (AREA)
  • Sliding-Contact Bearings (AREA)
  • X-Ray Techniques (AREA)

Claims (7)

  1. Drehanodentyp-Röntgenröhre mit:
    - einer Drehstruktur (12) mit zwei Enden mit einem Bodenabschnitt an einem Ende und einem Öffnungsabschnitt, der eine Öffnung eines Hohlzylinders (22, 23, 24) definiert, am anderen Ende und einer Drehwelle (13), die sich von dem Bodenabschnitt der Drehstruktur (12) erstreckt, und an der ein Anodentarget festgelegt ist,
    - einer stationären Struktur (15) mit einem säulenartigen Körper, der koaxial in die Drehstruktur (12) eingepaßt ist, mit einem freien Abstand zwischen der Innenfläche der Dreh- und der Außenfläche der stationären Struktur (12; 15) zum drehbaren Tragen der Drehstruktur (12),
    - einer Abstandsöffnung, die zwischen dem Öffnungsabschnitt der Drehstruktur (12) und der stationären Struktur (15) gebildet ist,
    - Lagerabschnitten (21), die zwischen der Dreh- und stationären Struktur (12; 15) vorgesehen sind,
    dadurch gekennzeichnet, daß
    - die Drehstruktur (12) einen ersten Hohldrehzylinder (22), der einen Bodenabschnitt hat, und einen zweiten Hohldrehzylinder (23), der den Öffnungsabschnitt hat und koaxial mit dem ersten Drehzylinder (22) zwischen dem ersten Drehzylinder (22) und der stationären Struktur (15) angeordnet ist, umfaßt, wobei der erste Drehzylinder (22) an seinem von dem Anodentarget entfernten Ende mit dem zweiten Drehzylinder (23) verbunden ist,
    - ein erster Wärmeisolierspalt (26) längs der Längsachse zwischen dem ersten und zweiten Drehzylinder (22, 23) und ein zweiter Wärmeisolierspalt (26) zwischen dem Bodenabschnitt und der Endfläche des zweiten Drehzylinders (23), die nahe dem Anodentarget ist, vorgesehen sind,
    - ein Ringblock (16) an dem Öffnungsabschnitt gesichert ist, um die Abstandsöffnung so zu umschließen, daß der Innenraum der Drehstruktur (12) abgeschlossen ist,
    - die Lagerabschnitte (21) durch Radialgleitlagerabschnitte und Druckgleitlagerabschnitte zwischen dem zweiten Drehzylinder (23) und der stationären Struktur (15) gebildet sind,
    - die Gleitlagerabschnitte Spiralrillen haben, die auf wenigstens einer Einheit aus dem zweiten Drehzylinder (23) und der stationären Struktur (15) gebildet sind,
    - die Lagerabschnitte (21) ein flüssiges Metallschmiermittel enthalten, das in einem flüssigen Zustand während einer Drehung der Drehstruktur (12) ist.
  2. Drehanodentyp-Röntgenröhre nach Anspruch 1, gekennzeichnet durch weiterhin ein äußerstes zylindrisches Glied (24), das koaxial auf der Außenfläche der Drehstruktur (12) positioniert ist.
  3. Drehanodentyp-Röntgenröhre nach Anspruch 1, dadurch gekennzeichnet, daß in dem Wärmeisolierspalt (26) längs der Längsachse zwischen den ersten und zweiten Drehzylindern (22, 23) ein Wärmeisoliermaterial angeordnet ist.
  4. Drehanodentyp-Röntgenröhre nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß die Drehstruktur (12) eine Einrichtung (27) umfaßt, um die Ausrichtung der ersten und zweiten Drehzylinder (22, 23) aufrechtzuerhalten.
  5. Drehanodentyp-Röntgenröhre mit:
    - einer stationären Struktur (15) mit einem Hohlzylinder, der einen Bodenabschnitt mit einem ersten zylindrischen Loch und einen Öffnungsabschnitt mit einem Scheibenblock (31), der den Öffnungsabschnitt schließt, hat,
    - einer Drehstruktur (33, 34), die koaxial in die stationäre Struktur (15) mit einem Abstand zwischen der Innenfläche der stationären Struktur (15) und der Außenfläche der Drehstruktur (12) angeordnet ist, wobei die Drehstruktur (12) drehbar durch die stationäre Struktur (15) getragen ist,
    - Lagerabschnitten, die zwischen der Dreh- und stationären Struktur (34; 15) vorgesehen sind,
    - einer Drehwelle (13), die sich von der Drehstruktur (33, 34) durch das erste zylindrische Loch erstreckt, wobei an der Drehwelle (13) ein Anodentarget (11) festgelegt ist,
    - einem Zylinder (32), der als ein Rotor arbeitet und an der Drehwelle (13) festgelegt ist sowie koaxial die stationäre Struktur umgibt,
    dadurch gekennzeichnet, daß
    - die Drehstruktur (33, 34) einen Hohldrehzylinder (34) mit einem offenen Ende, das von dem Anodentarget entfernt ist, und einem Endabschnitt, der näher zu dem ein zweites zylindrisches Loch aufweisenden Anodentarget gelegen ist, und einen säulenartigen Körper (33), der in den Drehzylinder (34) eingepaßt ist und an dem die Drehwelle (13) so festgelegt ist, daß sie sich durch das zweite zylindrische Loch erstreckt, umfaßt,
    - der Drehzylinder (34) an seinem von dem Anodentarget (11) entfernten Ende mit dem säulenartigen Körper (33) verbunden ist,
    - ein Wärmeisolierspalt (26) längs der Längsachse zwischen dem Drehzylinder (34) und dem säulenartigen Körper (33) und ein zweiter Wärmeisolierspalt zwischen dem Endabschnitt des Hohldrehzylinders (34) näher zu dem Anodentarget (11) und der gegenüberliegenden Endfläche des säulenartigen Körpers (33) vorgesehen sind,
    - die Lagerabschnitte durch Radial- und Gleitdrucklagerabschnitte (21) gebildet sind, die zwischen den Dreh- und stationären Strukturen (12; 15) vorgesehen sind und Spiralrillen haben;
    - die Gleitlagerabschnitte (21) ein flüssiges Metallschmiermittel enthalten, das in einem flüssigen Zustand während einer Drehung der Drehstruktur ist.
  6. Drehanoden-Röntgenröhre nach Anspruch 5, gekennzeichnet durch weiterhin:
    eine Rotorschicht (24), die koaxial mit der Außenfläche des Zylinders (32) verbunden ist, der koaxial die stationäre Struktur (15) umgibt und der an der Drehwelle (13) festgelegt ist.
  7. Drehanoden-Röntgenröhre nach Anspruch 5 oder 6, dadurch gekennzeichnet, daß der Hohldrehzylinder (34) und der säulenartige Körper (33) durch Vorsprünge (27) an dem Ende kontaktiert sind, das das Anodentarget (11) trägt, wobei die Vorsprünge (27) auf der Mantelfläche des säulenartigen Körpers (33) gebildet sind.
EP91116669A 1991-01-31 1991-09-30 Drehanoden-Röntgenröhre Expired - Lifetime EP0496945B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP11260/91 1991-01-31
JP1126091 1991-01-31

Publications (2)

Publication Number Publication Date
EP0496945A1 EP0496945A1 (de) 1992-08-05
EP0496945B1 true EP0496945B1 (de) 1996-07-03

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EP91116669A Expired - Lifetime EP0496945B1 (de) 1991-01-31 1991-09-30 Drehanoden-Röntgenröhre

Country Status (7)

Country Link
US (1) US5224142A (de)
EP (1) EP0496945B1 (de)
JP (1) JP3090359B2 (de)
KR (1) KR940009323B1 (de)
CN (1) CN1024872C (de)
CA (1) CA2052471C (de)
DE (1) DE69120651T2 (de)

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EP0565005B1 (de) * 1992-04-08 1996-12-11 Kabushiki Kaisha Toshiba Drehanoden-Röntgenröhre
US5541975A (en) * 1994-01-07 1996-07-30 Anderson; Weston A. X-ray tube having rotary anode cooled with high thermal conductivity fluid
DE4419697A1 (de) * 1994-06-04 1995-12-07 Philips Patentverwaltung Drehanoden-Röntgenröhre
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JP2002075260A (ja) 2000-06-15 2002-03-15 Toshiba Corp 回転陽極型ｘ線管及びそれを備えたｘ線管装置
WO2003019610A1 (en) * 2001-08-29 2003-03-06 Kabushiki Kaisha Toshiba Rotary positive pole type x-ray tube
US6707882B2 (en) 2001-11-14 2004-03-16 Koninklijke Philips Electronics, N.V. X-ray tube heat barrier
JP3795482B2 (ja) * 2003-08-29 2006-07-12 株式会社東芝 回転陽極型ｘ線管
ATE554498T1 (de) * 2007-08-16 2012-05-15 Koninkl Philips Electronics Nv Hybridentwurf für eine anodenplattenstruktur zur konfiguration einer hochleistungsröntgenröhre nach art einer rotierenden anode
US8774367B2 (en) * 2008-10-22 2014-07-08 Koninklijke Philips N.V. Bearing within an X-ray tube
US20100128848A1 (en) * 2008-11-21 2010-05-27 General Electric Company X-ray tube having liquid lubricated bearings and liquid cooled target
DE102009031530A1 (de) * 2009-07-02 2011-01-13 Siemens Aktiengesellschaft Gleitlager für hohe Drehgeschwindigkeiten eines Anodentellers
WO2011082836A1 (en) * 2010-01-11 2011-07-14 Siemens Aktiengesellschaft Direct drive wind turbine with a cooling system
JP5582975B2 (ja) * 2010-11-10 2014-09-03 株式会社東芝 回転陽極型ｘ線管
CN102462540A (zh) * 2010-11-15 2012-05-23 迈柯唯医疗设备(苏州)有限公司 一种医用旋转操作台装置
US8908833B2 (en) 2010-12-28 2014-12-09 Rigaku Corporation X-ray generator
US9972472B2 (en) * 2014-11-10 2018-05-15 General Electric Company Welded spiral groove bearing assembly
KR200495850Y1 (ko) * 2021-08-03 2022-09-01 주식회사 로이첸 교체형 도마

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DE3245455A1 (de) * 1981-12-09 1983-06-16 Hitachi, Ltd., Tokyo Roentgenroehre mit drehanode
EP0141475A1 (de) * 1983-11-08 1985-05-15 Koninklijke Philips Electronics N.V. Röntgenröhre mit einem Spiralrillenlager

Also Published As

Publication number Publication date
DE69120651T2 (de) 1996-12-19
JP3090359B2 (ja) 2000-09-18
JPH0513030A (ja) 1993-01-22
US5224142A (en) 1993-06-29
DE69120651D1 (de) 1996-08-08
CA2052471C (en) 1997-10-07
KR940009323B1 (ko) 1994-10-06
CN1024872C (zh) 1994-06-01
CA2052471A1 (en) 1992-08-01
CN1063776A (zh) 1992-08-19
KR920015416A (ko) 1992-08-26
EP0496945A1 (de) 1992-08-05

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